CN105090134A - Hydraulic supply apparatus - Google Patents
Hydraulic supply apparatus Download PDFInfo
- Publication number
- CN105090134A CN105090134A CN201510266098.XA CN201510266098A CN105090134A CN 105090134 A CN105090134 A CN 105090134A CN 201510266098 A CN201510266098 A CN 201510266098A CN 105090134 A CN105090134 A CN 105090134A
- Authority
- CN
- China
- Prior art keywords
- joint
- pressure
- valve
- tension loop
- switching position
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
- F16D48/066—Control of fluid pressure, e.g. using an accumulator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
- F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
- F16H61/0206—Layout of electro-hydraulic control circuits, e.g. arrangement of valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/027—Installations or systems with accumulators having accumulator charging devices
- F15B1/033—Installations or systems with accumulators having accumulator charging devices with electrical control means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/14—Fluid pressure control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
- F16H61/0025—Supply of control fluid; Pumps therefore
- F16H61/0031—Supply of control fluid; Pumps therefore using auxiliary pumps, e.g. pump driven by a different power source than the engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0203—Control by fluid pressure with an accumulator; Details thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0221—Valves for clutch control systems; Details thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2306/00—Shifting
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of Transmission Device (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
A hydraulic supply apparatus (1) for an automatic or automated transmission of a motor vehicle includes a high-pressure circuit (7) which has a pressure accumulator (9) and is supplied through the use of a high-pressure pump (3), a low-pressure circuit (6) which is supplied through the use of a low-pressure pump (2), wherein the high-pressure pump (3) and the low-pressure pump (2) are driven by a common drive unit (4), and a valve (10) which is provided downstream of the high-pressure pump (3). The valve (10) has three switching positions, wherein a supply to the high-pressure circuit (7) by the high-pressure pump (3) is possible in the first switching position, and the output end of the high-pressure pump (3) is connected to a reservoir (5) or to the input end of the high-pressure pump (3) in the second switching position. The high-pressure circuit (7) is connected to the reservoir (5) in the third switching position of the valve (10).
Description
Technical field
The present invention relates to a kind of for Motor Vehicle automatically or the hydraulic supply unit of the speed changer of automation, especially dual-clutch transmission, it has
-high tension loop, this high tension loop has accumulator and supplies by high-pressure service pump;
-low tension loop, this low tension loop supplies by low pressure pump, and wherein said high-pressure service pump and described low pressure pump are driven by common driver element;
-be arranged in the valve in described high-pressure service pump downstream, this valve has at least two switching position, the supply that wherein can realize for described high tension loop by described high-pressure service pump in first switching position, and described in second switch position, the outlet side of high-pressure service pump is connected with container or is connected with the suction side of described high-pressure service pump.
Background technique
That disclose vehicle transmission by the document EP1420185A2 forming described type, that there is high tension loop and low tension loop hydraulic supply unit, wherein by pump to each loop delivering fluids.Two pumps is driven by common driver element simultaneously.In each loop, arrange valve in the downstream of every platform pump, described valve has two switching position.In first switching position, described delivery side of pump side be connected with affiliated pressure circuit and described pump to described pressure circuit delivering fluids.If there is fluid demand and there is not fluid demand or enough pressure in another pressure circuit in a pressure circuit, so do not require that the valve in the pressure circuit of fluid is moved in its second switch position described.In described second switch position, described delivery side of pump side is connected with its suction side, and described pump runs thus and do not transport fluid in this pressure circuit in idle running.The energy ezpenditure of this pump declines and than much smaller when described pump must extrude superfluous fluid by pressure-limit valve thus.Implement flexible programs for two kinds of connection on disclose described valve and described pressure circuit fluid technique.In the first flexible program, the pressure circuit belonging in described second switch position also with the suction side of described pump in other words described container be connected.This causes following result: in this switching position, this pressure circuit to be switched in the state of fully pressure-free power and its pump must form described pressure again when there is pressure demand.Must connect described pump very continually and for a long time thus, this causes higher energy ezpenditure.
In described second flexible program, in the second switch position of described valve, affiliated pressure circuit and described delivery side of pump side cut off.Pressure is maintained in this pressure circuit, until its fluid consuming due to described load does not drop under threshold value.Then then must reclose described pump.The shortcoming of this flexible program is, it does not have the pressure drop that can realize being controlled in described pressure circuit.Especially the pressure obtaining maintaining in high tension loop then can be harmful to valve after the described Motor Vehicle that stops for the valve no longer moved in this pressure circuit.The similar layout of described valve also obtains open from DE102010018192A1, and wherein here described high tension loop is equipped with accumulator.Shorten the time of delivery of necessity of pump thus, but describe mentioned shortcoming simultaneously, because pressure acts on described valve for a long time with higher level.
Summary of the invention
Therefore task of the present invention is, so improves a kind of hydraulic supply unit with high tension loop and low tension loop, make its loss few and have efficiency, and it can realize pressure drop targetedly in described high tension loop.
This task is resolved in the following manner in conjunction with the preamble of claim 1: described valve has the 3rd switching position, and described in described 3rd switching position, high tension loop is connected with described container.According to demand, typically after the Motor Vehicle that stops, described valve can be switched in this switching position, can reduce the pressure in described high tension loop thus.Thus the valve in described high tension loop and other component unloaded and extend its working life.Do not need extra valve, simple, the with low cost and impact that is not easily interfered of described device thus.Generally supply final controlling element by described pressure duct, described final controlling element handles one or more clutch and shifting cylinder.If desired, described valve also can be used as safety valve, in the process run at Motor Vehicle in urgency by described safety valve when modulating valve is malfunctioning by emptying for described high tension loop, thus be such as separated described Power Train when clutch initiatively closes.
Accompanying drawing explanation
Have now different from designing and improving the feasible program of described supplier.For this reason, first with reference to being arranged on claim 1 following claim.By accompanying drawing and affiliated explanation, the multiple preferred design proposal to described hydraulic supply unit is explained in detail below.In accompanying drawing:
Fig. 1 illustrates the schematic hydraulic pipe line figure of the hydraulic supply unit according to the first embodiment of the present invention; And
Fig. 2 illustrates the schematic hydraulic pipe line figure of the hydraulic supply unit according to the second embodiment of the present invention.
Embodiment
Figure 1 illustrates a kind of hydraulic supply unit 1 of speed changer of the automation be not shown specifically for Motor Vehicle.The speed changer of described automation is especially configured to dual-clutch transmission.Described hydraulic supply unit 1 is correspondingly configured to and is suitable for described dual-clutch transmission.Described hydraulic supply unit 1 has the high tension loop 7 with accumulator 9, and described high tension loop 7 supplies by high-pressure service pump 3.In addition, described hydraulic supply unit 1 has low tension loop 6, and described low tension loop 6 supplies by low pressure pump 2.Described high tension loop 7 for hydraulically handling unshowned clutch device and gearshift (electromechanical integrated device) with pressure oil, and described low tension loop 6 to described clutch device, be that described speed changer is fed cold oil and/or lubricant oil if desired.Described high-pressure service pump 3 and described low pressure pump 2 are driven by common driver element 4, preferably motor.Described motor advantageously EC motor and can manipulating with arbitrary rotating speed.Described low pressure pump 3 and described high-pressure service pump 3 can be two levels of two pumps separated, a dual pump with high pressure teeth portion and low pressure teeth portion or a unique double stage tandem pump.The suction side of this two pumps is connected with container 5,5 ', wherein before described pump, also can arrange filtering mechanism and/or cooling mechanism if desired.Described two pumps can be unique with one common container be connected, or as shown in this embodiment, described high-pressure service pump 3 is connected with container 5 and described low pressure pump 2 is connected with container 5 '.At the arranged downstream valve 10 of described high-pressure service pump 3, this valve has at least three switching position.The guiding valve that described valve 10 is advantageously handled in an electromagnetic manner, but it also can be handled in a hydrodynamic manner.The outlet side of described high-pressure service pump 3 is connected with the first joint 11 of described valve 10 by the first pressure piping 21, and is connected with described high tension loop 7 by the second pressure piping 22, wherein in described second pressure piping 22, arranges safety check 8.Described high tension loop 7 is connected with the second joint 12 of described valve 10 by the 3rd pressure piping 23, and described accumulator 9 is connected with described 3rd pressure piping 23.Described valve 10 is had the 3rd joint the 13, three joint and is connected with described container 5 by the 4th pressure piping 24.Described 3rd joint 13 also can couple together with the suction side of described high-pressure service pump 3 by described 4th pressure piping 24.
In addition, described valve 10 has the 4th joint the 24, four joint and is connected with described container 5.Described 4th joint 14 is by the 5th pressure piping 25 and be connected with described container 5 by described 4th pressure piping 24, and wherein said 5th pipeline 25 also can directly import in described container 5 individually.Especially simply implement in flexible program in one, described valve 10 can be 3/3 valve, and wherein said 3rd joint 13 is connected with described 4th joint 14 and is connected with described container on fluid technique.
Described valve 10, advantageously by first switching position of spring pre-tightening, described first joint 11 and described second joint 12 are closed.Described oil is fed in described high tension loop 7 and described accumulator 9 by described second pressure piping 22 via described safety check 8 by described first pressure piping 11 by the outlet side of described high-pressure service pump 3.Thus, the supply for described high tension loop 7 can be realized by described high-pressure service pump 3.
If the enough and demand existed cold oil/lubricant oil of the pressure in described high tension loop, then move on to described valve 10 in its second switch position.In this switching position of described valve 10, described first joint 11 is connected with described 3rd joint 13 and described second joint 12 cuts out.Thus, the outlet side of described high-pressure service pump 3 is connected with described container 5, and described high-pressure service pump 3 does not have mineralization pressure and only consumes less energy.In described high tension loop 7, keep described pressure, because described second pressure piping 22 is closed by described safety check 8, and described 3rd pressure piping 23 is closed by described valve 10.Oil can be transported in described low tension loop 6 by described low pressure pump 2.
In the 3rd switching position of described valve 10, described second joint 12 is connected with described 4th joint 14, and described high tension loop 7 to be connected with described container 5 by described 3rd pressure piping 23 and described accumulator 9 is drained thus.Pressure in described high tension loop 7 is lowered in desired level, is advantageously lowered to external pressure.Thus the valve of described high tension loop and other component are unloaded and extend its working life.
Described valve 10 also can so be arranged, makes it not have the 4th joint 14 and the second joint 12 is connected with described 3rd joint 13 described in its 3rd switching position.
In the 3rd switching position of described valve 10, the outlet side of described high-pressure service pump 3 can advantageously be connected with its suction side or described container 5.Described first joint 11 is connected with described 3rd joint 13 in this switching position of described valve 10, and the outlet side of described high-pressure service pump 3 is connected with described container 5 by described first pressure piping 21 and described 4th pressure piping 24 thus.Even if also pressure drop fast can be realized in described high tension loop 7 in this operation when described high-pressure service pump 3 runs, that is at Motor Vehicle.Also described valve 10 can be used as safety valve thus.Certainly, described first joint 11 also can be connected with described 4th joint 14.
Fig. 2 shows the second embodiment according to hydraulic supply unit 1 of the present invention.Only the difference relative to Fig. 1 is inquired into.
The outlet side of described high-pressure service pump 3 is connected with the first joint 11 of described valve 10 by the first pressure piping 11, wherein in described first pressure piping 21, arranges safety check 8.High tension loop 7 is connected with the second joint 12 of described valve 10 by the second pressure piping 22, and described second pressure piping is also connected to described accumulator 9.Described valve is had the 3rd joint the 13, three joint and is connected with the suction side of described high-pressure service pump 3 by the 3rd pressure piping 23.But described 3rd joint 13 also can be connected with described container 5.In addition, described valve 10 has the 4th joint the 14, four joint and is connected with described container 5.
Described valve 10, advantageously by first switching position of spring pre-tightening, described first joint 11 is connected with described second joint 12.Described oil to be fed in described high tension loop 7 and described accumulator 9 by described second pressure piping 22 via described safety check 8 and described valve 10 by described pressure piping 11 by the outlet side of described high-pressure service pump 3.The supply that can realize for described high tension loop 7 by described high-pressure service pump 3 thus.
In the second switch position of described valve 10, described first joint 11 is connected with described 3rd joint 13, and described second joint 12 cuts out.The outlet side of described high-pressure service pump 3 is connected with its suction side thus, and described high-pressure service pump does not have mineralization pressure and only consumes less energy.Described pressure is kept, because described second pressure piping 22 is closed by described valve 10 in described high tension loop 7.Described oil can be transported in described low tension loop 6 by described low pressure pump.
In the 3rd switching position of described valve 10, described second joint 12 is connected with described 4th joint 14.Described high tension loop 7 to be connected with described container 5 by described second pressure piping 22 and described 4th pressure piping 24 and described accumulator 9 is drained.Pressure in described high tension loop 7 is lowered in desired level.
In the 3rd switching position of described valve 10, the outlet side of described high-pressure service pump 3 is advantageously connected with its suction side or described container 5.Described first joint 11 is connected with described 3rd joint 13 in this switching position of described valve 10, and the outlet side of described high-pressure service pump 3 is connected with the suction side of described high-pressure service pump 3 with described 3rd pressure piping 23 by described first pressure piping 21 thus.Even if this also can realize pressure drop faster when described driver element 4 drives described pump in described high tension loop 7.Also described valve 10 can be used as safety valve thus.Certainly, described first joint 11 also can be connected with described 4th joint 14.
In a kind of mode of execution of remodeling, also can abandon the 4th joint 14 of described valve 10 and abandon described 4th pressure piping 24, wherein described in the 3rd switching position of described valve 10, the second joint 12 is connected with described 3rd joint 13.The pressure of the accumulator 9 of described high tension loop 7 is then reduced by described 3rd pipeline.In this modification advantageously, described 3rd pressure piping 23 is connected with described container 5, can realize unrestricted pressure drop.
Flexible program shown in Figure 1, that have the 4th connected pressure piping 24 and the 5th pressure piping 25 has following advantage: can test the speed changer of described hydraulic supply unit 1 or described automation on test stand, its mode is: be connected to by described 4th pipeline 24 on outside pressure supply unit.By these stress-free pipelines in normal operation, supply necessary pressure when not depending on revolution speed to described high tension loop 7.The intensive valve of volume flowrate (such as speed changer gear operation valve) can be reduced thus, for the low on fuel temporarily provided in described accumulator 9 described valve for drafting continuous print characteristic curve in described high tension loop 7.
Certainly, described in the second embodiment according to Fig. 2, the 3rd pressure piping 23 also can correspondingly be connected with described 4th pressure piping 24, and wherein said 3rd pressure piping 23 and described 4th pressure piping 24 are not then connected with the suction side of high-pressure service pump 3 but are connected with described container 5.
" pressure piping " this statement not should narrow sense to must be pipe or closed passage go like that understand, described in a kind of extreme flexible program, be in the pressure piping among being connected with container 5 present only by the joint of valve, the oil of outflow then arrives in described container without pressure ground.
If described, the pressure piping (the 4th pressure piping 24 in such as Fig. 1 and the 3rd pressure piping 23 in Fig. 2) that first pressure piping 11 unloads is connected with the suction side of described high-pressure service pump 3, so advantageously, the described offloading pipeline (the 5th pressure piping 25 in such as Fig. 1 and the 4th pressure piping 24 in Fig. 2) being used for the pressure drop of high tension loop 7 is separately formed.That is, generally arrange various different filtering mechanism at the suction side of described high-pressure service pump 3 between described container 5, described filtering mechanism produces certain pressure drag.Can by being connected to come quickly with described container 5 or the direct of external pressure and implement the pressure drop in described high tension loop 7 when not depending on the current state of described filtering mechanism.
Claims (10)
1. for Motor Vehicle automatically or the hydraulic supply unit (1) of the speed changer of automation, have
-high tension loop (7), described high tension loop has accumulator (9) and supplies by high-pressure service pump (3);
-low tension loop (6), described low tension loop supplies by low pressure pump (2), and wherein said high-pressure service pump (3) and described low pressure pump (2) are driven by common driver element (4);
-be arranged in the valve (10) in described high-pressure service pump (3) downstream, described valve has at least two switching position, the supply that wherein can realize for described high tension loop (7) by described high-pressure service pump (3) in first switching position, and the outlet side of high-pressure service pump (3) is connected with container (5) or is connected with the suction side of described high-pressure service pump (3) described in second switch position, it is characterized in that, described valve (10) has the 3rd switching position, and described in described 3rd switching position, high tension loop (7) is connected with described container (5).
2. by hydraulic supply unit according to claim 1 (1), it is characterized in that, the outlet side of described high-pressure service pump (3) is connected with first joint (11) of described valve (10) by the first pressure piping (21) and is connected with described high tension loop (7) by the second pressure piping (22), wherein in described second pressure piping (22), arrange safety check (8), described high tension loop (7) is connected with second joint (12) of described valve (10) by the 3rd pressure piping (23), described valve (10) has the 3rd joint (13), described 3rd joint is connected with described container (5) by the 4th pressure piping (24) or is connected with the suction side of described high-pressure service pump (3), wherein described in first switching position of described valve (10), the first joint (11) cuts out with described second joint (12) and the first joint (11) is connected with described 3rd joint (12) and described second joint (12) cuts out described in the second switch position of described valve (10).
3., by hydraulic supply unit according to claim 2 (1), it is characterized in that, described in the 3rd position of described valve (10), the second joint (12) is connected with described 3rd joint (13).
4. by hydraulic supply unit according to claim 2 (1), it is characterized in that, described valve (10) has the 4th joint (14), described 4th joint is connected with described container (5), and the second joint (12) is connected with described 4th joint (14) described in the 3rd switching position of described valve (10).
5. by hydraulic supply unit according to claim 1 (1), it is characterized in that, the outlet side of described high-pressure service pump (3) is connected with first joint (11) of described valve (10) by the first pressure piping (21), described high tension loop (3) is connected with second joint (12) of described valve (10) by the second pressure piping (22), described valve (10) has the 3rd joint (13), described 3rd joint is connected with described container (5) by the 3rd pressure piping (23) or is connected with the suction side of described high-pressure service pump (3), wherein described in first switching position of described valve (10), the first joint (11) is connected with described second joint (12), and the first joint (11) is connected with described 3rd joint (13) and described second joint (12) cuts out described in the second switch position of described valve (10).
6., by hydraulic supply unit according to claim 5 (1), it is characterized in that, described in the 3rd switching position of described valve (10), the second joint (12) is connected with described 3rd joint (13).
7. by hydraulic supply unit according to claim 5 (1), it is characterized in that, described valve (10) has the 4th joint (14), described 4th joint is connected with described container (5), and the second joint (12) is connected with described 4th joint (14) described in the 3rd switching position of described valve (10).
8., by the hydraulic supply unit (1) according to any one of claim 5 to 7, it is characterized in that, in described first pressure piping (21), arrange safety check (8).
9., by the hydraulic supply unit (1) according to any one of claim 2 to 8, it is characterized in that, described in the 3rd switching position of described valve (10), the first joint (11) is connected with described 3rd joint (13).
10. Motor Vehicle, has with the speed changer by the automatic of hydraulic supply unit in any one of the preceding claims wherein (1) or automation.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014209856.4 | 2014-05-23 | ||
| DE102014209856.4A DE102014209856A1 (en) | 2014-05-23 | 2014-05-23 | Hydraulic supply device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105090134A true CN105090134A (en) | 2015-11-25 |
| CN105090134B CN105090134B (en) | 2018-01-19 |
Family
ID=54431780
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510266098.XA Active CN105090134B (en) | 2014-05-23 | 2015-05-22 | Hydraulic supply unit |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US10018235B2 (en) |
| CN (1) | CN105090134B (en) |
| DE (1) | DE102014209856A1 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107939786A (en) * | 2017-12-22 | 2018-04-20 | 重庆青山工业有限责任公司 | Double-clutch automatic gearbox hydraulic oil supply system and motor vehicle |
| CN109027207A (en) * | 2018-09-19 | 2018-12-18 | 重庆青山工业有限责任公司 | A kind of automatic transmission hydraulic oil supply system |
| CN109084016A (en) * | 2018-10-08 | 2018-12-25 | 重庆长安汽车股份有限公司 | A kind of DCT speed changer double pump system, control method and automobile |
| CN109099155A (en) * | 2018-10-08 | 2018-12-28 | 重庆长安汽车股份有限公司 | A kind of DCT speed changer double pump system, control method and automobile |
| CN109237013A (en) * | 2018-10-08 | 2019-01-18 | 重庆长安汽车股份有限公司 | A kind of DCT transmission hydraulic control system, method and automobile |
| CN109340074A (en) * | 2018-10-18 | 2019-02-15 | 中国海洋石油集团有限公司 | A kind of hydraulic control system |
| CN113280057A (en) * | 2020-02-20 | 2021-08-20 | Fte汽车有限责任公司 | Assembly for actuating a clutch in a motor vehicle transmission |
| CN114341516A (en) * | 2019-09-27 | 2022-04-12 | 舍弗勒技术股份两合公司 | Method for controlling a friction clutch and torque transmission device comprising such a friction clutch |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6546211B2 (en) * | 2016-04-01 | 2019-07-17 | 株式会社山田製作所 | Hydraulic control device and control method therefor |
| CN109236760A (en) * | 2017-05-26 | 2019-01-18 | 天津滨海光热跟踪技术有限公司 | A kind of two-ram hydraulic drive system |
| DE102018219170A1 (en) | 2018-11-09 | 2020-05-14 | Volkswagen Aktiengesellschaft | Oil system, in particular oil system for a motor vehicle, with a low pressure branch and with a high pressure branch |
| DE102019201709A1 (en) * | 2019-02-11 | 2020-08-13 | Volkswagen Aktiengesellschaft | Oil system, in particular oil system for a motor vehicle, with a valve for filling a high-pressure branch reservoir from a low-pressure branch |
| DE102019204858A1 (en) * | 2019-04-04 | 2020-10-08 | Magna Pt B.V. & Co. Kg | Hydraulic system and method for controlling the same |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1420185A2 (en) * | 2002-11-18 | 2004-05-19 | ZF Sachs AG | Vehicle drive train comprising a pumping arrangement in order to supply a clutch device with a pressurised fluid |
| US20040211378A1 (en) * | 2002-05-03 | 2004-10-28 | Udo Diehl | Pressure-supply device for an electrohydraulic valve control of gas-exchange valves in internal combustion engines |
| US20090321209A1 (en) * | 2007-03-07 | 2009-12-31 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydraulic arrangement for controlling a twin-clutch transmission of a motor vehicle |
| CN102292574A (en) * | 2009-01-23 | 2011-12-21 | 戴姆勒股份公司 | Control device for an automated geared transmission |
| CN102483151A (en) * | 2009-08-06 | 2012-05-30 | 舍弗勒技术股份两合公司 | Hydraulic System For Hydraulically Controlling A Dual Clutch Transmission |
| DE102011100796A1 (en) * | 2011-05-06 | 2012-11-08 | Audi Ag | Clutch transmission i.e. double clutch transmission, for passenger car, has cooling circuit, and filter attached to pumps as common filter, where pump of cooling circuit is connected with electric motor over separating element |
| CN103502695A (en) * | 2011-05-06 | 2014-01-08 | 奥迪股份公司 | Clutch transmission |
| CN103502696A (en) * | 2011-05-06 | 2014-01-08 | 奥迪股份公司 | Method for operating a clutch transmission, clutch transmission |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| NL171084C (en) * | 1972-09-13 | 1983-02-01 | Reintjes Eisenwerke | HYDRAULICALLY OPERABLE FLAP COUPLER, IN PARTICULAR FOR SHIP-REVERSING GEARS. |
| US4924983A (en) * | 1987-12-10 | 1990-05-15 | Kubota, Ltd. | Propelling clutch apparatus for a working vehicle |
| GB9608256D0 (en) * | 1996-04-20 | 1996-06-26 | Ap Kongsberg Holdings Ltd | Actuation systems |
| WO2010127659A1 (en) | 2009-05-06 | 2010-11-11 | Schaeffler Technologies Gmbh & Co. Kg | Hydraulic energy source for supplying a downstream hydraulic system with hydraulic energy |
-
2014
- 2014-05-23 DE DE102014209856.4A patent/DE102014209856A1/en active Pending
-
2015
- 2015-05-22 US US14/719,449 patent/US10018235B2/en active Active
- 2015-05-22 CN CN201510266098.XA patent/CN105090134B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20040211378A1 (en) * | 2002-05-03 | 2004-10-28 | Udo Diehl | Pressure-supply device for an electrohydraulic valve control of gas-exchange valves in internal combustion engines |
| EP1420185A2 (en) * | 2002-11-18 | 2004-05-19 | ZF Sachs AG | Vehicle drive train comprising a pumping arrangement in order to supply a clutch device with a pressurised fluid |
| US20090321209A1 (en) * | 2007-03-07 | 2009-12-31 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydraulic arrangement for controlling a twin-clutch transmission of a motor vehicle |
| CN102292574A (en) * | 2009-01-23 | 2011-12-21 | 戴姆勒股份公司 | Control device for an automated geared transmission |
| CN102483151A (en) * | 2009-08-06 | 2012-05-30 | 舍弗勒技术股份两合公司 | Hydraulic System For Hydraulically Controlling A Dual Clutch Transmission |
| DE102011100796A1 (en) * | 2011-05-06 | 2012-11-08 | Audi Ag | Clutch transmission i.e. double clutch transmission, for passenger car, has cooling circuit, and filter attached to pumps as common filter, where pump of cooling circuit is connected with electric motor over separating element |
| CN103502695A (en) * | 2011-05-06 | 2014-01-08 | 奥迪股份公司 | Clutch transmission |
| CN103502696A (en) * | 2011-05-06 | 2014-01-08 | 奥迪股份公司 | Method for operating a clutch transmission, clutch transmission |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107939786A (en) * | 2017-12-22 | 2018-04-20 | 重庆青山工业有限责任公司 | Double-clutch automatic gearbox hydraulic oil supply system and motor vehicle |
| CN109027207A (en) * | 2018-09-19 | 2018-12-18 | 重庆青山工业有限责任公司 | A kind of automatic transmission hydraulic oil supply system |
| CN109084016A (en) * | 2018-10-08 | 2018-12-25 | 重庆长安汽车股份有限公司 | A kind of DCT speed changer double pump system, control method and automobile |
| CN109099155A (en) * | 2018-10-08 | 2018-12-28 | 重庆长安汽车股份有限公司 | A kind of DCT speed changer double pump system, control method and automobile |
| CN109237013A (en) * | 2018-10-08 | 2019-01-18 | 重庆长安汽车股份有限公司 | A kind of DCT transmission hydraulic control system, method and automobile |
| CN109237013B (en) * | 2018-10-08 | 2020-09-08 | 重庆长安汽车股份有限公司 | DCT (discrete cosine transformation) transmission hydraulic control system and method and automobile |
| CN109084016B (en) * | 2018-10-08 | 2020-12-29 | 重庆长安汽车股份有限公司 | DCT transmission double-pump system, control method and automobile |
| CN109340074A (en) * | 2018-10-18 | 2019-02-15 | 中国海洋石油集团有限公司 | A kind of hydraulic control system |
| CN114341516A (en) * | 2019-09-27 | 2022-04-12 | 舍弗勒技术股份两合公司 | Method for controlling a friction clutch and torque transmission device comprising such a friction clutch |
| US11873870B2 (en) | 2019-09-27 | 2024-01-16 | Schaeffler Technologies AG & Co. KG | Method for controlling a friction clutch, and torque transmission device comprising same |
| CN113280057A (en) * | 2020-02-20 | 2021-08-20 | Fte汽车有限责任公司 | Assembly for actuating a clutch in a motor vehicle transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| US10018235B2 (en) | 2018-07-10 |
| CN105090134B (en) | 2018-01-19 |
| DE102014209856A1 (en) | 2015-11-26 |
| US20150337914A1 (en) | 2015-11-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105090134A (en) | Hydraulic supply apparatus | |
| KR101339230B1 (en) | Hydraulic control system for transmission | |
| CN102168753B (en) | Transmission hydraulic control system having a pump bypass valve | |
| JP5487513B2 (en) | Hydraulic control device for mechanical automatic transmission | |
| JP5418547B2 (en) | Fluid pressure control device for automatic transmission | |
| CN102102758A (en) | Method of operating an auxiliary electric pump | |
| CN103946594A (en) | Oil pressure control device | |
| CN101907165A (en) | The hydraulic supply unit of automatic transmission | |
| US8915076B2 (en) | Transmission hydraulic control system having flow augmentation | |
| RU2013112874A (en) | HYDRAULIC REGULATOR FOR VEHICLE DRIVE SYSTEM | |
| CN110167780A (en) | The hydraulic clutch actuating system to oil with on-demand clutch | |
| CN101260938A (en) | Automobile electric control mechanical type automatic speed variator hydraulic system and its control method | |
| CN103717946A (en) | Hydraulic controller for an automatic transmission of a motor vehicle | |
| CN102767618A (en) | Transmission of a motor vehicle, having an input shaft and an output shaft | |
| JP2012207752A (en) | Hydraulic control device | |
| CN106151500A (en) | gear box hydraulic control system | |
| CN103883573B (en) | Jib hydraulic control system and port loading and unloading machinery | |
| CN103119337A (en) | Fluid pressure control device | |
| CN107923522A (en) | The hydraulic system of automatic transmission | |
| JP5233956B2 (en) | Oil supply device | |
| CN104508330B (en) | Gear box hydraulic loop | |
| CN107965572B (en) | Electro-hydraulic control system for automatic transmission | |
| JP5910760B2 (en) | Hydraulic control device | |
| CN107816546A (en) | A kind of method of hydraulic control system of automatic speed changer and the application system | |
| CN106352060A (en) | Torque converter clutch release fluid lubrication |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |